U.S. patent number 6,604,906 [Application Number 09/921,314] was granted by the patent office on 2003-08-12 for centrifugal multiblade blower.
This patent grant is currently assigned to Calsonic Kansei Corporation. Invention is credited to Masaharu Onda, Yukio Ozeki, Toshio Yajima.
United States Patent |
6,604,906 |
Ozeki , et al. |
August 12, 2003 |
Centrifugal multiblade blower
Abstract
A centrifugal multiblade blower includes a first counter-flow
prevention means that prevents part of air flowing through a scroll
chamber from flowing through a first aperture defined between a
multiblade fan and a suction-side case plate of a scroll casing
back to a suction port, and a second counter-flow prevention means
that prevents part of air flowing through the scroll chamber from
flowing through a second aperture defined between the multiblade
fan and a motor-side case plate of the scroll casing back to the
upstream side of the scroll chamber. A length L1 of the scroll
chamber measured in the motor-shaft axial direction is dimensioned
to be longer than a length L2 of the multiblade fan measured in the
motor-shaft axial direction. Additionally the scroll chamber is
gradually enlarged toward a discharge port of the casing.
Inventors: |
Ozeki; Yukio (Tochigi,
JP), Onda; Masaharu (Tochigi, JP), Yajima;
Toshio (Tochigi, JP) |
Assignee: |
Calsonic Kansei Corporation
(Tokyo, JP)
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Family
ID: |
18729169 |
Appl.
No.: |
09/921,314 |
Filed: |
August 3, 2001 |
Foreign Application Priority Data
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Aug 4, 2000 [JP] |
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2000-237277 |
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Current U.S.
Class: |
415/204; 415/206;
417/370; 416/189; 416/186R |
Current CPC
Class: |
F04D
29/162 (20130101); F04D 25/082 (20130101); F04D
29/4233 (20130101) |
Current International
Class: |
F04D
25/08 (20060101); F04D 29/42 (20060101); F04D
25/02 (20060101); F04D 29/08 (20060101); F04D
29/16 (20060101); F04D 029/28 (); F04B
039/06 () |
Field of
Search: |
;415/204,206,208.3
;416/186R,189 ;417/370 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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0 589 300 |
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Mar 1994 |
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EP |
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0 846 868 |
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Jun 1998 |
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EP |
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64-41700 |
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Feb 1989 |
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JP |
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2002021790 |
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Jan 2002 |
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JP |
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WO 9009524 |
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Aug 1990 |
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WO |
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Primary Examiner: Look; Edward K.
Assistant Examiner: Edgar; Richard A.
Attorney, Agent or Firm: Foley & Lardner
Claims
What is claimed is:
1. A centrifugal multiblade blower comprising: a multiblade fan
having a fan motor; a scroll casing that accommodates the
multiblade fan; a first counter-flow prevention structure
comprising a first annular fan rib on one of an upper side of the
fan and the scroll casing, and a first annular recess formed in the
other of the upper side of the fan and the scroll casing into which
the first annular rib extends; a second counter-flow prevention
structure comprising a second annular fan rib provided on one of a
lower side of the fan and the scroll housing, the second annular
fan rib extending into a second annular recess formed in the other
of the lower side of the fan and the scroll casing; a cooling
passage structure which includes a case disposed about the motor,
the cooling passage having an upstream end fluidly communicated
with the scroll casing downstream of the fan at a first location of
high static pressure and a downstream end which includes a space
enclosed by the lower side of the fan and the second annular fan
rib, and which is communicated with the scroll casing at a second
location of low static pressure.
2. A centrifugal multiblade blower comprising: a multiblade fan (2)
having a plurality of blades (2a); a fan motor (3) having a motor
shaft (3a) on which the multiblade fan (2) is mounted; a scroll
casing (4) that accommodates therein the multiblade fan (2) and has
a discharge port (4c) and cooperates with an outer periphery of the
multiblade fan (2) to define a spiral scroll chamber (4a); the
casing comprising: (i) a suction-side case plate (4d) having a
suction port (4b); and (ii) a motor-side case plate (4e) which is
located opposite to the suction-side case plate (4d) in such a
manner as to sandwich the multiblade fan (2) between the
suction-side case plate (4d) and the motor-side case plate (4e),
and on which a motor body (3b) of the fan motor (3) is mounted; a
first counter-flow prevention means (10) for preventing part of air
flowing through the scroll chamber (4a) from flowing through a
first aperture (G1) defined between the multiblade fan (2) and the
suction-side case plate (4d) back to the suction port (4b); a
second counter-flow prevention means (20) for preventing part of
air flowing through the scroll chamber (4a) from flowing through a
second aperture (G2) defined between the multiblade fan (2) and the
motor-side case plate (4e) back to an upstream side of the scroll
chamber (4a); a length (L1) of the scroll chamber (4a) measured in
an axial direction of the motor shaft (3a) being dimensioned to be
longer than a length (L2) of the multiblade fan (2) measured in the
axial direction of the motor shaft (3a), and the scroll chamber
(4a) being gradually enlarged toward the discharge port (4c) of the
casing (4); the second counter-flow prevention means (20)
comprising: (i) a second fan rib (21) provided on the multiblade
fan (2) so that the second fan rib is protruded from the multiblade
fan (2) to the second aperture (G2), and coaxially arranged with
respect to the axis of the multiblade fan (2) and extending
completely in the circumferential direction of the multiblade fan
(2) around an entire circumference of an outer peripheral portion
of a base of the multiblade fan (2) facing a rear end of the motor
shaft (3a); and (ii) a second case rib (22) provided on the
motor-side caseplate (4e) so that the second case rib (22) is
protruded from the motor-side case plate (4e) to the second
aperture (G2), and coaxially arranged with and radially spaced
apart from the second fan rib (21), and extending completely in the
circumferential direction of the multiblade fan (2) so that the
second fan rib (21) and the second case rib (22) are located close
to and radially spaced from each other by a predetermined distance;
a motor protective case (3c) that protects the motor body (3b); a
motor cooling passage system using a pressure differential between
a pressure in a high-pressure area of the scroll chamber having a
comparatively high pressure and a pressure in a low-pressure area
of the scroll chamber having a lower pressure than the pressure in
the high-pressure area, the motor cooling passage system
comprising: (i) a communication portion (6) that intercommunicates
an interior space of the motor body (3b) and the high-pressure area
of the scroll chamber; (ii) a cut-out portion (23) formed in the
second case rib (22) and exposed to the low-pressure area of the
scroll chamber to intercommunicate the low-pressure area of the
scroll chamber and a space (S) which is defined between the
motor-side case plate (4e) and the multiblade fan (2) and into
which a portion of the motor body (3b) is exposed; and (iii) at
least one communication hole (3d), which is formed at a portion of
the motor protective case (3c) exposed into the space (S) and
through which the interior space of the motor body (3b) and the
space (S) are intercommunicated.
3. The centrifugal multiblade blower as claimed in claim 2, wherein
the scroll chamber (4a) is gradually enlarged in the axial
direction of the motor shaft (3a) at an axial enlargement angle
(.alpha.) representative of a magnitude of enlargement of the
scroll chamber (4a) in the axial direction of the motor shaft (3a)
toward the discharge port (4c), and additionally the scroll chamber
(4a) is gradually enlarged in a radial direction of the multiblade
fan (2) at a radial enlargement angle (n) representative of a
magnitude of enlargement of the scroll chamber (4a) in the radial
direction of the multiblade fan (2) from a tongue portion (4k) of
the scroll casing (4) toward the discharge port (4c), the radial
enlargement angle (n) being defined by an expression R=R.sub.0
exp{n(.theta.+.theta..sub.0)}, where R denotes a radius of the
scroll casing (4), R.sub.0 denotes a radius of the multiblade fan
(2), .theta. denotes an angle measured in a direction of rotation
of the multiblade fan (2) from a central point (P) of the tongue
portion (4k) that defines a narrowest portion of the scroll chamber
(4a), and .theta..sub.0 denotes an angle from a point (Q) across
which the length (L1) of the scroll chamber (4a) measured in the
axial direction of the motor shaft (3a) begins to enlarge to the
central point (P) of the tongue portion (4k).
4. The centrifugal multiblade blower as claimed in claim 3, wherein
the axial enlargement angle (.alpha.) of the scroll chamber (4a) is
set at substantially 6 degrees.
5. The centrifugal multiblade blower as claimed in claim 4, wherein
the radial enlargement angle (n) of the scroll chamber (4a) is set
at substantially 3.3 degrees.
6. The centrifugal multiblade blower as claimed in claim 5, wherein
the scroll chamber (4a) is gradually uniformly enlarged in opposite
axial directions of the motor shaft (3a) at the axial enlargement
angle (.alpha.) of substantially 6 degrees from the tongue portion
(4k) toward the discharge port (4c).
7. The centrifugal multiblade blower as claimed in claim 2,
wherein: the first counter-flow prevention means (10) comprises:
(i) a first fan rib (11) provided on the multiblade fan (2) so that
the first fan rib (11) is protruded from the multiblade fan (2) to
the first aperture (G1), and coaxially arranged with respect to an
axis of the multiblade fan (2) and extending completely in a
circumferential direction of the multiblade fan (2) around an
entire circumference of n outer peripheral curved surface portion
normal to and adjacent to a perimeter of a p of the multiblade fan
(2) facing a front end of the motor shaft (3a); and (ii) a first
case rib (12) provided on the suction-side case plate (4d) so that
the first case rib (12) is protruded from the suction-side case
plate (4d) to the first aperture (G1), and coaxially arranged with
and radially spaced apart from the first fan rib (11), and
extending completely in the circumferential direction of the
multiblade fan (2) so that the first fan rib (11) and the first
case rib (12) are located close to each other and radially spaced
from each other by a predetermined distance.
8. The centrifugal multiblade blower as claimed in claim 7, wherein
the first fan rib (11) is formed as a cylindrical fan rib having an
I shape in cross section, and the first case rib (12) is formed as
an inverted U shaped first case rib that covers the first fan rib
(11) and has a pair of radially opposing, inner and outer rib wall
portions between which the first fan rib (11) is located in close
proximity to each of the radially opposing, inner and outer rib
wall portions.
9. The centrifugal multiblade blower as claimed in claim 6, wherein
the first fan rib (11) is formed as a rimmed annular fan rib having
a L shape in cross section and coaxially arranged with respect to
the axis of the multiblade fan (2) and extending completely in the
circumferential direction of the multiblade fan (2) around the
entire circumference of the perimeter of the top of the multiblade
fan (2), and the first case rib (12) comprises: (i) a first rib
portion (12a) formed as an inverted U shaped case rib portion that
covers the rimmed annular fan rib with a predetermined clearance,
and coaxially located close to the first fan rib (11) so that the
first rib portion (12a) and the first fan rib (11) are radially
spaced from each other by a predetermined distance on both sides of
the rimmed annular fan rib; (ii) a second rib portion (12b) formed
as a radially-extending annular flat-faced rib portion formed
integral with the suction-side case plate (4d) and extending
radially outwards from an outer periphery of the inverted U shaped
case rib portion and located parallel to and close to the perimeter
of the top of the multiblade fan (2) by a predetermined distance;
(iii) a third rib portion (12c) formed as a substantially
cylindrical rib portion formed integral with the suction-side case
plate (4d) and extending perpendicular to the radially-extending
annular flat-faced rib portion and located adjacent to the
circumference of the outer peripheral curved surface portion normal
to and adjacent to the perimeter of the top of the multiblade fan
(2) by a predetermined distance.
Description
TECHNICAL FIELD
The present invention relates to a centrifugal multiblade blower
suitable to an automotive air conditioning system.
BACKGROUND ART
In automotive air conditioning systems, there is usually employed a
centrifugal multiblade blower fan installed upstream of an air
duct. One such centrifugal multiblade blower has been disclosed in
Japanese Patent Provisional Publication No. 64-41700 (corresponding
to Japanese Patent No. 2690731). FIG. 7 is a cross section showing
the structure of the centrifugal multiblade blower disclosed in the
Japanese Patent No. 2690731. Centrifugal multiblade blower a shown
in FIG. 7 is comprised of a multiblade fan b formed with a
plurality of blades b1, a blower fan motor c, and a scroll casing d
that accommodates therein the multiblade fan b and defines a scroll
chamber d1 between the inner periphery of the casing and the outer
periphery of the multiblade fan. Multiblade fan b is installed onto
a motor shaft c1 of fan motor c. Casing d is formed into a
logarithmic spiral shape and comprised of a suction-side case plate
d3 formed with a suction port d2 and a fan-motor-side case plate d4
located opposite to the suction-side case plate d3. A motor body c2
of fan motor c is attached to the motor-side case plate d4. The
radius R of the logarithmic spiral scroll casing is generally
defined by an expression R=R.sub.0 exp{n(.theta.+.theta..sub.0)},
where R.sub.0 denotes a radius of the multiblade fan, .theta.
denotes an angle measured in the direction of rotation of the
multiblade fan from a central point of a tongue portion of scroll
casing that defines the narrowest portion of the scroll chamber,
.theta..sub.0 denotes an angle from a point across which a length
L1 of the scroll chamber (often called a scroll width) measured in
the axial direction of the motor shaft begins to enlarge to the
central point of the scroll-casing tongue portion, and n denotes a
so-called enlargement angle that represents the magnitude of
enlargement of the scroll chamber in the radial direction of the
multiblade fan (see FIG. 6). In centrifugal multiblade blower fans
used for automotive air conditioning systems, the enlargement angle
n is usually set to range from 5 degrees (8.72.times.10.sup.-2
radians) to 8 degrees (14.0.times.10.sup.-2 radians). As is
generally known, the volumetric capacity of the scroll chamber
tends to increase, as the enlargement angle n increases, and thus
the scroll casing is enlarged in the radial direction of the
multiblade fan. In other words, the volumetric capacity of the
scroll chamber tends to decrease, as the enlargement angle n
decreases, and thus the scroll casing is reduced. For the reasons
set out above, with the enlargement angle n set to a comparatively
smaller angle, it is possible to down-size the scroll casing, but
the volumetric capacity of the scroll chamber tends to decrease
undesirably. Owing to the decreased volumetric capacity of the
scroll chamber, during operation of the centrifugal multiblade
blower, there is an increased tendency for the counter-flow rate of
air flowing from a suction-side aperture G1 defined between the
multiblade fan b and the suction-side case plate d3 toward the
suction port d2 to increase. At the same time, there is an
increased tendency for the counter-flow rate of air flowing from a
motor-side aperture G2 defined between the multiblade fan b and the
motor-side case plate d4 toward the upstream side of the scroll
chamber d1 to increase. Therefore, in the centrifugal multiblade
blower a, although the scroll casing can be down-sized by reducing
the enlargement angle n of the scroll chamber, the fan efficiency
is reduced. Additionally, due to the reduced enlargement angle n,
the pressure in the scroll chamber tends to become unstable. This
may increase noises and vibrations during operation of the
multiblade fan.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the invention to provide a
centrifugal multiblade blower, which avoids the aforementioned
disadvantages.
It is another object of the invention to provide a centrifugal
multiblade blower, which is capable of down-sizing a scroll casing
by reducing a so-called enlargement angle of a scroll chamber,
without lowering a fan efficiency and without increasing noises and
vibrations.
In order to accomplish the aforementioned and other objects of the
present invention, a centrifugal multiblade blower comprises a
multiblade fan having a plurality of blades, a fan motor having a
motor shaft on which the multiblade fan is mounted, a scroll casing
that accommodates therein the multiblade fan and has a discharge
port and cooperates with an outer periphery of the multiblade fan
to define a spiral scroll chamber, the casing comprising a
suction-side case plate having a suction port, and a motor-side
case plate which is located opposite to the suction-side case plate
in such a manner as to sandwich the multiblade fan between the
suction-side case plate and the motor-side case plate, and on which
a motor body of the fan motor is mounted, a first counter-flow
prevention means for preventing part of air flowing through the
scroll chamber from flowing through a first aperture defined
between the multiblade fan and the suction-side case plate back to
the suction port, and a second counter-flow prevention means for
preventing part of air flowing through the scroll chamber from
flowing through a second aperture defined between the multiblade
fan and the motor-side case plate back to an upstream side of the
scroll chamber, wherein a length of the scroll chamber measured in
an axial direction of the motor shaft is dimensioned to be longer
than a length of the multiblade fan measured in the axial direction
of the motor shaft, and the scroll chamber is gradually enlarged
toward the discharge port of the casing. It is preferable that the
scroll chamber is gradually enlarged in the axial direction of the
motor shaft at an axial enlargement angle .alpha. representative of
a magnitude of enlargement of the scroll chamber in the axial
direction of the motor shaft toward the discharge port, and
additionally the scroll chamber is gradually enlarged in a radial
direction of the multiblade fan at a radial enlargement angle n
representative of a magnitude of enlargement of the scroll chamber
in the radial direction of the multiblade fan from a tongue portion
of the scroll casing toward the discharge port. The radial
enlargement angle n is defined by an expression R=R.sub.0
exp{n(.theta.+.theta..sub.0)}, where R denotes a radius of the
scroll casing, R.sub.0 denotes a radius of the multiblade fan,
.theta. denotes an angle measured in a direction of rotation of the
multiblade fan from a central point of the tongue portion that
defines the narrowest portion of the scroll chamber, and
.theta..sub.0 denotes an angle from a point across which the length
of the scroll chamber measured in the axial direction of the motor
shaft begins to enlarge to the central point of the tongue
portion.
The other objects and features of this invention will become
understood from the following description with reference to the
accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a perspective view illustrating a first embodiment of the
centrifugal multiblade blower of the invention.
FIG. 2 is a cross-sectional view taken along the line II--II of
FIG. 1.
FIG. 3 is an explanatory view explaining a predetermined axial
enlargement angle .alpha. representative of the magnitude of
enlargement of the scroll chamber in the axial direction of the
motor shaft.
FIG. 4 is a graph showing a blower fan performance of the
centrifugal multiblade blower of the first embodiment of FIG.
1.
FIG. 5 is a cross-sectional view illustrating a second embodiment
of the centrifugal multiblade blower of the invention.
FIG. 6 is a plan view illustrating the centrifugal multiblade
blower fan of the first embodiment of FIGS. 1 and 2.
FIG. 7 is a cross-sectional view illustrating the conventional
centrifugal multiblade blower.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings, particularly to FIGS. 1, 2, and 6,
the centrifugal multiblade blower 1 of the first embodiment is
exemplified in an automotive air conditioning system. Centrifugal
multiblade blower 1 is comprised of a multiblade fan 2, a blower
fan motor 3, and a logarithmic spiral scroll casing 4. Multiblade
fan 2 is formed with a plurality of blades 2a, and accommodated in
scroll casing 4. As best shown in FIG. 2, multiblade fan 2 is
installed onto or fixedly connected to one end of a motor shaft 3a
of fan motor 3. A motor body 3b of fan motor 3 is attached to or
mounted in scroll casing 4. Multiblade fan 2 has a conical plate
portion 2b. Conical plate 2b is fixedly connected to the motor
shaft end by means of a bolt and a nut, in such a manner as to
cover a portion of motor body 3b (the upper motor-body portion in
FIG. 2). Fan motor 3 is equipped with a motor protective case 3c
that protects a rotor and a stator incorporated in the motor body.
Motor body 3b is wholly covered and protected by means of
protective case 3c. Scroll casing 4 defines a spiral scroll chamber
4a between the inner periphery of casing 4 and the outer periphery
of multiblade fan 2. Scroll casing 4 is formed with a suction port
(air inlet) 4b through which air is sucked in or drawn into the
multiblade fan, and a discharge port (air outlet) 4c through which
the air is discharged from scroll chamber 4a toward outside of the
casing. As clearly shown in FIG. 2, casing 4 is comprised of a
suction-side case plate 4d formed with the suction port 4b, a
motor-side case plate 4e located opposite to the suction-side case
plate 4d in such a manner as to sandwich the multiblade fan between
the two opposing case plates 4d and 4e, and an outer peripheral
wall plate 4f formed continuously with both the two opposing case
plates 4d and 4e and joining them so as to form an outer peripheral
wall of scroll chamber 4a. Motor body 3b is attached to or mounted
on the motor-side case plate 4e. As viewed from the plan view shown
in FIG. 6, the structure of scroll chamber 4a of centrifugal
multiblade blower 1 of the first embodiment is similar to that of
the conventional centrifugal multiblade blower. That is, the radius
R of the logarithmic spiral scroll casing 4 is defined by an
expression R=R.sub.0 exp{n(.theta.+.theta..sub.0)}, where R.sub.0
denotes a radius of the multiblade fan 2, .theta. denotes an angle
measured in the direction of rotation of the multiblade fan 2 from
a central point P of a tongue portion 4k of scroll casing 4 that
defines the narrowest portion of the scroll chamber 4a,
.theta..sub.0 denotes an angle from a point Q across which a length
L1 of the scroll chamber 4a (often called a scroll width) measured
in the axial direction of the motor shaft 3a begins to enlarge to
the central point P of the scroll-casing tongue portion 4k, and n
denotes a so-called enlargement angle that represents the magnitude
of enlargement of the scroll chamber 4a in the radial direction of
the multiblade fan. The enlargement angle n representative of the
magnitude of enlargement of scroll chamber 4a in the radial
direction of multiblade fan 2 will be hereinafter referred to as a
"radial enlargement angle n". In centrifugal multiblade blower fans
used for automotive air conditioning systems, the radial
enlargement angle n is usually set to range from 5 degrees
(8.72.times.10.sup.-2 radians) to 8 degrees (14.0.times.10.sup.-2
radians). As fully described later in detail, in the centrifugal
multiblade fan of the shown embodiment, note that the radial
enlargement angle n of scroll chamber 4a is set at substantially
3.3 degrees. Returning to FIG. 2, the length L1 of scroll chamber
4a measured in the axial direction of motor shaft 3a is dimensioned
to be longer than the length L2 of multiblade fan 2 measured in the
axial direction of motor shaft 3a. Additionally, the scroll chamber
4a is gradually enlarged in the axial direction of motor shaft 3a
as well as in the radial direction of multiblade fan 2 from the
scroll-casing tongue portion 4k toward discharge port 4c.
Referring now to FIG. 3, there is shown the explanatory view used
to explain how the scroll chamber is enlarged particularly in the
axial direction of motor shaft 3a. In FIG. 3, the hypothetical
straight line M1 indicates a line that the circumference of each of
the substantially annular top and the substantially annular base of
multiblade fan 2 is extended straight, whereas the hypothetical
straight line M2 indicates a line that the logarithmic spiral outer
circumference of each of the spiral top (or the upper inner
peripheral wall portion) and the spiral base (or the lower inner
peripheral wall portion) of scroll chamber 4a is extended straight
in the same direction as the hypothetical line M1. The angle
.alpha. between the two straight lines M1 and M2 means an axial
enlargement angle that represents the magnitude of enlargement of
scroll chamber 4a in the axial direction of motor shaft 3a. In
other words, the axial enlargement angle .alpha. indicates how the
length L1 of scroll chamber 4a measured in the axial direction of
motor shaft 3a is enlarged from the scroll-casing tongue portion 4k
toward discharge port 4c. In the centrifugal multiblade blower 1 of
the first embodiment, the axial enlargement angle .alpha. is set at
substantially 6 degrees.
As discussed above, in the centrifugal multiblade blower 1 of the
first embodiment, as best seen in FIGS. 1 and 2, the scroll chamber
4a is axially uniformly enlarged on both sides at the axial
enlargement angle .alpha.(.apprxeq.6.degree.) from the
scroll-casing tongue portion 4k toward discharge port 4c.
Therefore, as compared to the scroll chamber of the conventional
centrifugal multiblade blower shown in FIG. 7, the volumetric
capacity of the scroll chamber 4a of centrifugal multiblade blower
1 of the first embodiment increases in the axial direction of motor
shaft 3a. In the centrifugal multiblade blower of the first
embodiment, on the other hand, the previously-described radial
enlargement angle n is set at a relatively small angle such that
the volumetric capacity of scroll chamber 4a is decreased by a
volumetric capacity equivalent to the increase of the volumetric
capacity of scroll chamber 4a (in the motor-shaft axial direction)
arising from the axial enlargement angle .alpha.. Actually, in the
multiblade blower 1 of the first embodiment, the radial enlargement
angle n is set at substantially 3.3 degrees.
In FIG. 2, reference sign G1 denotes a suction-side aperture
defined between the multiblade fan 2 and the suction-side case
plate 4d. In multiblade blower 1 of the first embodiment, a first
counter-flow prevention means 10 is provided to prevent part of air
flowing through scroll chamber 4a from flowing through the
suction-side aperture G1 back to the suction port 4b. First
counter-flow prevention means 10 is comprised of a first fan rib 11
and a first case rib 12. First fan rib 11 is formed integral with
or fixedly connected onto or provided on multiblade fan 2 so that
the first fan rib is protruded from the multiblade fan 2 to the
suction-side aperture G1. In more detail, first fan rib 11 is
formed as a circumferentially continuously extending cylindrical
fan rib which has an I shape in cross section and is coaxially
arranged with respect to the axis of blower fan 2 and extends
completely in the circumferential direction of multiblade fan 2
around the entire circumference of the outer peripheral curved
surface portion normal to and adjacent to the perimeter of the
substantially annular top of multiblade fan 2 facing the
screw-threaded tip end (front end) of motor shaft 3a. On the other
hand, first case rib 12 is provided on or formed integral with
suction-side case plate 4d so that the first case rib is protruded
from the suction-side case plate 4d to the suction-side aperture
G1. First case rib 12 is coaxially arranged with and radially
spaced apart from first fan rib 11 and extends completely
continuously in the circumferential direction of multiblade fan 2
so that the first fan rib 11 and the first case rib 12 are located
close to each other and radially spaced from each other by a
predetermined slight distance. As can be appreciated from the cross
section of FIG. 2, first case rib 12 is formed at the
circumferential edge portion of suction port 4d of suction-side
case plate 4d. First case rib 12 has an inverted U shape in cross
section that covers the cylindrical first fan rib 11. The
inverted-U shaped first case rib 12 has a pair of radially
opposing, inner and outer rib wall portions between which the
cylindrical first fan rib 11 is located. First fan rib 11 is
located in close proximity to each of the two radially opposing rib
wall portions of inverted-U shaped first case rib 12. In other
words, the radial distance between the first fan rib 11 and each of
the two radially opposing rib wall portions of inverted-U shaped
first case rib 12 is set at a predetermined small distance. The
inner rib wall portion of the two radially opposing rib wall
portions of inverted-U shaped first case rib 12 is formed as a
bellmouth portion 4g of suction port 4b. In FIG. 2, reference sign
G2 denotes a motor-side aperture defined between the multiblade fan
2 and the motor-side case plate 4e. In the multiblade blower 1 of
the first embodiment, in addition to the previously-noted first
counter-flow prevention means 10, a second counter-flow prevention
means 20 is provided to prevent part of air flowing through scroll
chamber 4a from flowing through the motor-side aperture G2 back to
the upstream side of scroll chamber 4a. Second counter-flow
prevention means 20 is comprised of a second fan rib 21 and a
second case rib 22. Second fan rib 21 is formed integral with or
fixedly connected onto or provided on multiblade fan 2 so that the
second fan rib is protruded from the multiblade fan 2 to the
motor-side aperture G2. In more detail, second fan rib 21 is formed
as a circumferentially continuously extending cylindrical fan rib
which is coaxially arranged with respect to the axis of the
multiblade fan 2 and extends completely in the circumferential
direction of multiblade fan 2 around the entire circumference of
the outer peripheral portion of the substantially annular base of
multiblade fan 2 facing the rear end of motor shaft 3a. On the
other hand, second case rib 22 is provided on or formed integral
with motor-side case plate 4e so that the second case rib is
protruded from the motor-side case plate 4e to the motor-side
aperture G2. Second case rib 22 is coaxially arranged with and
radially spaced apart from second fan rib 21 and extends completely
continuously in the circumferential direction of multiblade fan 2,
so that the second fan rib 21 and the second case rib 22 are
located close to and radially spaced from each other by a
predetermined slight distance. In the multiblade blower of the
first embodiment shown in FIGS. 1 and 2, second case rib 22 has a
cut-out portion 23 (fully described later). As can be appreciated
from the cross section of FIG. 2, second case rib 22 is formed on a
substantially flat plate surface of the motor-side case plate 4e
facing the read end surface or the base surface 2c of conical plate
2b. Motor-side case plate 4e is formed at its central portion with
a cylindrical motor holding portion 4h having a cylindrical bore
closed at one end. Motor holding portion 4h is provided to hold fan
motor 3. The cylindrical opening end portion of motor holding
portion 4h is coaxially arranged with both the second fan rib 21
and the second case rib 22, so that the outer periphery of the
cylindrical opening end portion of motor holding portion 4h is
surrounded by both the second fan rib 21 and the second case rib
22. Fan motor 3 is installed on the motor-side case plate 4e by
fitting the motor body 3b into the motor holding portion 4h. A
space S is defined between the motor-side case plate 4e and the
conical plate 2b of multiblade fan 2. The motor-shaft portion (the
upper portion of motor protective case 3c) of fan motor 3 is
exposed from the cylindrical opening end of motor holding portion
4h into the space S. At least one motor first communication hole 3d
is formed in a portion of motor protective case 3c, exposed from
the opening end of motor holding portion 4h into the space S. In
the shown embodiment, as seen in FIG. 2, a plurality of motor first
communication holes 3d are formed in a portion of motor protective
case 3c. Motor first communication hole 3d is provided to
intercommunicate the space S and the interior space of motor body
3b. A motor second communication hole 3e is also provided in the
motor protective case 3c such that the motor second communication
hole 3e is located near the closed end of motor holding portion 4h.
Motor second communication hole 3e is provided to intercommunicate
the interior and exterior of motor body 3b. On the other hand,
motor holding portion 4h has a motor-holding-portion communication
hole 4i formed therein such that the motor-holding-portion
communication hole 4i conforms to the motor second communication
hole 3e. Motor-holding-portion communication hole 4i is provided to
communicate the interior space of motor body 3b via motor second
communication hole 3e and motor-holding-portion communication hole
4i with the exterior of the motor holding portion 4h. Motor-side
case plate 4e is formed with a case communication hole 4j located
near the discharge port 4c of scroll casing 4. Case communication
hole 4j is provided to intercommunicate the interior and exterior
of scroll chamber 4a. As can be seen from the cross section of FIG.
2, the motor-holding-portion communication hole 4i and the case
communication hole 4j are communicated with each other via a
communication member 5 attached to the motor-side case plate
4e.
As discussed above, scroll chamber 4a is gradually enlarged in
cross section from the from the scroll-casing tongue portion 4k
toward discharge port 4c. By virtue of the gradually enlarged cross
section of the scroll chamber, part of kinetic energy given to the
air drawn from the suction port 4b into the interior of scroll
casing 4 by means of the multiblade fan 2 is converted into static
pressure. Thus, an air-passage area in scroll chamber 4a close to
the discharge port 4c serves as the highest pressure area (simply,
high-pressure area). The previously-noted case communication hole
4j is provided at the high-pressure area of scroll chamber 4a
adjacent to discharge port 4c. Therefore, a part of air in the
high-pressure area of scroll chamber 4a is introduced through the
case communication hole 4j, motor-holding-portion communication
hole 4i, motor second communication hole 3e into the interior space
of the motor body 3b. Thereafter, the air introduced into the
interior of motor body flows through motor first communication
holes 3d into the space S. That is, the case communication hole 4j,
communication member 5, motor-holding-portion communication hole
4i, and motor second communication hole 3e cooperate with each
other to provide a communication portion 6 through which the
high-pressure area of scroll chamber 4a and the interior space of
motor body 3b of fan motor 3 are communicated with each other. The
previously-noted second case rib 22 is formed with the cut-out
portion 23 which is exposed to a low-pressure area of scroll
chamber 4a having a lower pressure than the pressure in the
high-pressure area of the scroll chamber. Second-case-rib cut-out
portion 23 is provided to intercommunicate the space S and the
low-pressure area of scroll chamber 4a. Thus, a part of air flowing
through the high-pressure area of scroll chamber 4a flows via the
communication portion 6 into the interior space of motor body 3b,
and passes through the interior of motor body 3b, and then flows
from first communication holes 3d into the space S defined in
conical plate 2b. Thereafter, the air further flows from the
cut-out portion 23 of second case rib 22 back to the low-pressure
area of scroll chamber 4a.
Referring now to FIG. 4, there is shown comparison between the
performance of the centrifugal multiblade blower with and without
the first and second counter-flow prevention means 10 and 20. The
axis of ordinate (y-coordinate) of the graph of FIG. 4 indicates a
discharge pressure (unit: Pa) in a tested point of a straight air
duct connected to the discharge port 4c of scroll casing 4. The
tested point of the straight air duct is spaced apart from the
discharge port 4c by a predetermined distance. The axis of
abscissas (x-coordinate) of the graph of FIG. 4 indicates a
discharge air quantity per minute (unit: m.sup.3 /min) of the air
discharged from the discharge port 4c. In FIG. 4, the upper
polygonal solid line indicates the performance of the centrifugal
multiblade blower of the first embodiment with first and second
counter-flow prevention means 10 and 20, whereas the lower
polygonal broken line indicates the performance of the centrifugal
multiblade blower without first and second counter-flow prevention
means 10 and 20. The multiblade blower indicated by the lower
polygonal broken line has almost the same structure as the
multiblade blower indicated by the upper polygonal solid line,
except that first and second counter-flow prevention means 10 and
20 are not provided. As can be appreciated from comparison between
the upper and lower blower performance characteristic curves of
FIG. 4, under the condition that the same discharge air quantity
must be attained, the discharge pressure created by the multiblade
blower with the first and second counter-flow prevention means is
higher than that created by the multiblade blower without the first
and second counter-flow prevention means. As discussed above, the
radial enlargement angle n of scroll chamber 4a of centrifugal
multiblade blower 1 of the first embodiment is set at substantially
3.3 degrees. When considering the blower-performance test result of
FIG. 4, note that the upper blower performance characteristic curve
obtained by the multiblade blower of the first embodiment (having
radial enlargement angle n set at substantially 3.3 degrees and
equipped with first and second counter-flow prevention means 10 and
20) is substantially identical to the blower performance
characteristic curve obtained by the conventional multiblade blower
(having radial enlargement angle n set at substantially 6.3 degrees
and the same scroll-chamber volumetric capacity as the first
embodiment and not equipped with first and second counter-flow
prevention means 10 and 20).
As set forth above, in the centrifugal multiblade blower 1 of the
first embodiment, the radial enlargement angle n of scroll chamber
4a is set at substantially 3.3 degrees and thus the distance
between the outer peripheral wall plate 4f of scroll casing 4 and
the multiblade fan 2 is dimensioned to be shorter than that of the
conventional multiblade blower having radial enlargement angle n
set at substantially 6.3 degrees. For the reasons set out above,
assuming that the multiblade blower 1 of the first embodiment
having radial enlargement angle n set at substantially 3.3 degrees
is not equipped with first and second counter-flow prevention means
10 and 20, the counter-flow rate of air flowing from scroll chamber
4a via suction-side aperture G1 back to suction port 4b, and the
counter-flow rate of air flowing from scroll chamber 4a via
motor-side aperture G2 back to the upstream side of scroll chamber
4a both tend to increase rather than the conventional multiblade
blower with the scroll chamber having radial enlargement angle n
set at substantially 6.3 degrees and without the first and second
counter-flow prevention means. In this case (with radial
enlargement angle n set at substantially 3.3 degrees and without
first and second counter-flow prevention means 10 and 20), as shown
in the lower polygonal broken line of FIG. 4, the blower
performance deteriorates. Although radial enlargement angle n of
scroll chamber 4a is set at substantially 3.3 degrees, centrifugal
multiblade blower 1 of the first embodiment is actually equipped
with first and second counter-flow prevention means 10 and 20.
Therefore, in centrifugal multiblade blower 1 of the first
embodiment, it is possible to maintain its blower performance at
the same performance as the conventional multiblade blower having
radial enlargement angle n set at substantially 6.3 degrees and the
same scroll-chamber volumetric capacity as the first embodiment and
not equipped with first and second counter-flow prevention means 10
and 20.
As will be appreciated from the above, in centrifugal multiblade
blower 1 of the first embodiment, the length L1 of scroll chamber
4a measured in the motor-shaft axial direction is dimensioned to be
longer than the length L2 of multiblade fan 2 measured in the
motor-shaft axial direction, and additionally the scroll chamber 4a
is gradually enlarged in the motor-shaft axial direction (at the
axial enlargement angle .alpha. such as approximately 6 degrees)
from the scroll-casing tongue portion 4k toward discharge port 4c.
Therefore, even when the size of the scroll casing 4 measured in
the radial direction of multiblade fan 2 is reduced by decreasing
the radial enlargement angle n in comparison with the conventional
multiblade blower, owing to the axial enlargement angle .alpha. set
at approximately 6 degrees a cross-sectional area of a cross
section of scroll chamber 4a cut along a radial plane radially
extending from the axis of motor shaft 3a can be set to be
substantially identical to that of the conventional multiblade
blower. Also, even when the radial enlargement angle n of scroll
chamber 4a is set at a comparatively small value such as
substantially 3.3 degrees, the counter-flow of air flowing from
scroll chamber 4a via suction-side aperture G1 back to suction port
4b is suppressed or prevented by means of first counter-flow
prevention means 10. Additionally, the counter-flow of air flowing
from scroll chamber 4a via motor-side aperture G2 back to the
upstream side of scroll chamber 4a is suppressed or prevented by
means of second counter-flow prevention means 20. By the provision
of first and second counter-flow prevention means 10 and 20, even
in the multiblade blower with the scroll chamber having radial
enlargement angle n set at substantially 3.3 degrees it is possible
to maintain the blower fan total efficiency at the same level as
the conventional multiblade blower with the scroll chamber having
radial enlargement angle n set at substantially 6.3 degrees. By
effectively reducing both (i) the counter-flow rate of air flowing
from scroll chamber 4a via suction-side aperture G1 back to suction
port 4b, and (ii) the counter-flow rate of air flowing from scroll
chamber 4a via motor-side aperture G2 back to the upstream side of
scroll chamber 4a by way of first and second counter-flow
prevention means 10 and 20, it is possible to reducing undesired
noises and vibrations to the same noise/vibration level as the
conventional multiblade blower with the scroll chamber having a
comparatively great radial enlargement angle. In this manner, in
centrifugal multiblade blower 1 of the first embodiment, the scroll
casing 4 can be down-sized in the radial direction of multiblade
fan 2 by decreasing radial enlargement angle n. Furthermore, in
multiblade blower 1 of the first embodiment, first counter-flow
prevention means 10 is comprised of first fan rib 11 and first case
rib 12, and additionally first case rib 12 is coaxially arranged
with and radially spaced apart from first fan rib 11 and extends
completely continuously in the circumferential direction of
multiblade fan 2 so that first fan rib 11 and first case rib 12 are
located close to each other and radially spaced from each other by
a predetermined slight distance or a predetermined slight space or
a predetermined slight gap. The predetermined slight gap defined
between the two adjacent first ribs (11, 12) is effective to
suppress or prevent air flowing through scroll chamber 4a from
flowing through suction-side aperture G1 back to suction port 4b.
In a similar manner, in multiblade blower 1 of the first
embodiment, second counter-flow prevention means 20 is comprised of
second fan rib 21 and second case rib 22, and additionally second
case rib 22 is coaxially arranged with and radially spaced apart
from second fan rib 21 and extends completely continuously in the
circumferential direction of multiblade fan 2 so that second fan
rib 21 and second case rib 22 are located close to each other and
radially spaced from each other by a predetermined slight distance
or a predetermined slight space or a predetermined slight gap. The
predetermined slight gap defined between the two adjacent second
ribs (21, 22) is effective to suppress or prevent air flowing
through scroll chamber 4a from flowing through motor-side aperture
G2 back to the upstream side of scroll chamber 4a. In order to
effectively cool the fan motor, second case rib 22 is formed with
cut-out portion 23. As discussed above, second-case-rib cut-out
portion 23 is exposed to a low-pressure area of scroll chamber 4a
having a comparatively low pressure. Thus, there is less
counter-flow from second-case-rib cut-out portion 23 to the
upstream side of scroll chamber 4a, and therefore it is possible to
effectively suppress or prevent the counter-flow from motor-side
aperture G2 to the upstream side of scroll chamber 4a by way of the
two adjacent second ribs (21, 22). Also, in multiblade blower 1 of
the embodiment, a part of air flowing through the high-pressure
area of scroll chamber 4a is effectively used in order to
efficiently cool the interior of motor body 3b. Actually, a motor
cooling air passage is constructed such that a part of air flows
through communication portion 6 into the interior of motor body 3b,
and passing through the interior space of motor body 3b, and
flowing through motor first communication holes 3d into the space S
defined conical plate 2b, and then flows from second-case-rib
cut-out portion 23 back to the low-pressure area of scroll chamber
4a. Thus, it is possible more effectively cool the interior of
motor body 3b by way of circulating flow of a part of air flowing
through the high-pressure area of scroll chamber 4a from the
high-pressure side of scroll chamber 4a through communication
portion 6 via the interior of motor body 3b to the low-pressure
side of scroll chamber 4a. Additionally, in multiblade blower 1 of
the first embodiment, first fan rib 11 of first counter-flow
prevention means 10 is formed on the outer peripheral curved
surface portion normal to and adjacent to the perimeter of the
substantially annular top of multiblade fan 2 facing the
screw-threaded tip end of motor shaft 3a. Thus, it is possible to
minimize or reduce the flow resistance of air introduced through
suction port 4b into scroll casing 4, while maintaining suction
port 4b at as wide an opening area as possible. This enhances the
blower fan total efficiency and reduces noises and vibrations.
Referring now to FIG. 5, there is shown the centrifugal multiblade
blower of the second embodiment. The multiblade blower of the
second embodiment of FIG. 5 is similar to the multiblade blower of
the first embodiment of FIGS. 1 and 2, except that the shape and
structure of first fan rib 11 and first case rib 12 both
constructing first counter-flow prevention means 10 differ. Thus,
the same reference signs used to designate elements in the
multiblade blower of the first embodiment shown in FIGS. 1 and 2
will be applied to the corresponding reference signs used in the
multiblade blower of the second embodiment shown in FIG. 5, for the
purpose of comparison of the first and second embodiments. Detailed
description of the same elements will be omitted because the above
description thereon seems to be self-explanatory. In the multiblade
blower of the second embodiment of FIG. 5, first fan rib 11
constructing part of first counter-flow prevention means 10 is
formed as a rimmed annular fan rib which has a L shape in cross
section and is coaxially arranged with respect to the axis of
blower fan 2 and extends completely continuously in the
circumferential direction of multiblade fan 2 around the entire
circumference of the perimeter of the substantially annular top of
multiblade fan 2 facing the screw-threaded tip end of motor shaft
3a. On the other hand, first case rib 12 provided on or formed
integral with suction-side case plate 4d is comprised of first,
second, and third rib portions 12a, 12b, and 12c. First rib portion
12a has an inverted-U shape in cross section that covers the
axially circumferentially extending rimmed portion of first fan rib
11 with a predetermined clearance or a predetermined aperture, and
coaxially located close to first fan rib 11 so that first rib
portion 12a and first fan rib 11 are radially spaced from each
other by a predetermined slight distance on both sides of the
axially circumferentially extending rimmed portion of first fan rib
11. Second rib portion 12b is formed as a radially-extending
annular flat-faced rib portion formed integral with suction-side
case plate 4d and extending radially outwards from the outer
periphery of inverted-U shaped rib portion 12a and located parallel
to and close to the perimeter of the substantially annular top of
multiblade fan 2 facing the screw-threaded tip end of motor shaft
3a by a predetermined slight distance. Third rib portion 12c is
formed as a substantially cylindrical rib portion formed integral
with suction-side case plate 4d and extending perpendicular to
annular flat-faced second rib portion 12b and located adjacent to
the circumference of the outer peripheral curved surface portion
normal to and adjacent to the perimeter of the substantially
annular top of multiblade fan 2 facing the screw-threaded tip end
of motor shaft 3a by a predetermined slight distance. In the
multiblade blower of the second embodiment, due to rimmed annular
first fan rib 11 having a L shape in cross section and the cross
section of first case rib 12 contoured with respect to the L-shaped
rimmed annular first fan rib 11, first fan rib 11 and first case
rib 12 are coaxially located close to each other and axially as
well as radially spaced from each other by a predetermined slight
distance or a predetermined slight space or a predetermined slight
gap. The total length of the predetermined slight gap defined
between the two adjacent first ribs (11, 12) of the multiblade
blower of the second embodiment is longer than that of the first
embodiment. The multiblade blower of the second embodiment is
superior to that of the first embodiment in the ability to reduce
the counter-flow rate of air flowing from scroll chamber 4a via
suction-side aperture G1 back to suction port 4b. In other words,
the blower fan total efficiency of the multiblade blower of the
second embodiment is more enhanced rather than that of the first
embodiment. In the multiblade blower of the second embodiment, it
is possible to more effectively reduce undesired noises and
vibrations during operation of the multiblade fan.
In the centrifugal multiblade blower 1 of the first embodiment, the
scroll chamber 4a is axially uniformly enlarged on both sides (in
opposite axial directions of motor shaft 3a) at the axial
enlargement angle .alpha.(.apprxeq.6.degree.) from the
scroll-casing tongue portion 4k toward discharge port 4c. In lieu
thereof, the scroll chamber 4a is axially enlarged on one side (in
one axial direction of motor shaft 3a) at an axial enlargement
angle .alpha. from the scroll-casing tongue portion 4k toward
discharge port 4c. In order to minimize fluctuations in the
velocity of air discharged from the discharge port 4c, it is more
preferable that the scroll chamber 4a is axially uniformly enlarged
on both sides (in opposite axial directions of motor shaft 3a) at
the axial enlargement angle .alpha.(.apprxeq.6.degree.) from the
scroll-casing tongue portion 4k toward discharge port 4c.
The entire contents of Japanese Patent Application No. P2000-237277
(filed Aug. 4, 2000) is incorporated herein by reference.
While the foregoing is a description of the preferred embodiments
carried out the invention, it will be understood that the invention
is not limited to the particular embodiments shown and described
herein, but that various changes and modifications may be made
without departing from the scope or spirit of this invention as
defined by the following claims.
* * * * *